Drive systems for winch mechanisms



June 11, 1968 R VAN Dig-HEY ET A1. 3,387,823

DRIVE SYSTEMS FOR WINCH MECHANISMS nz/enzrs:- Roche l/zwf- Neg fweaemk. l/lflesonf.

June l, 1968 R. VAN Dra-HEY ET AL 3,387,823

DRIVE SYSTEMS FOR WINCH MECHANISMS Filed Jan. 5, 1967 Sheets-Sheet f@ edemji Fifa/650m June 1l, 1968 R. VAN DE-HEY ET Al. 3,387,823

DRIVE SYSTEMS FOR WINCH MECHANISMS Filed Jan. 3, 1967 3 Sheets-Sheet 3 AIISTRACT F THE DISCLOSURE Winch drive system embodying a pime mover for effecting selective rotation of an output shaft through transmission means associated with one end of the prime mover and together with clutch means associated with the output shaft and cable winding drums for effecting rotation of the cable winding drums in the same direction of rotation as the output shaft. A winch drive system having a clutch controlled cable winding drum together with `auxiliary drive means driven from the other end of lthe prime mover to effect rotation of another cable winding drum and/or the selective rotation of a platform upon which several cable `winding drums are mounted.

The present invention relates to drive systems for winch mechanisms for effecting certain swing and hoist functions required in the handling of a wide variety and different kinds of material handling operations and loads.

Presently known drive systems for winch mechanisms are unsatisfactory in many respects. Of particular disadvantage in such known systems -is the arrangement of a cable winding drum and drum shaft therefore in which the drum shaft is rotatably mounted in bearings supported on a frame or bed of the machine together with an arrangement of brake and clutch means for clutching the cable winding drum to the drum shaft or for holding the cable winding drum against rotation by brake means `associated with the drum. In current crane constructions, such bearings, clutches and brakes entail an expensive assembly and these several components must be frequently manually 'lubricated to function properly and prevent damage to them. ln many cases another person, in addition to the operator of the crane, is required primarily for purposes of lubricating the foregoing components so that two persons are needed as a 4minimum to operate a crane. Also known winch mechanisms lack of flexibility of safe and easy control such, for example, as rot-ating the bed of the crane carrying a boom simultaneously with lowering or raising of the boom. Further in presently known crane constructions mechanisms for controlling the rate of descent of the boom are unsatisfactory. Also, the winch mechanisms of the prior art, especially in arrangements embodying a plurality of cable winding drums, require heavy and cumbersome supporting frames or beds to adequately support the rotating cable winding drums and drum shafts and the loads imposed thereon.

According to Athe present invention, the foregoing and other disadvantages of presently known drive systems for winch mechanisms have been overcome and, importantly, in this regard the present invention concerns the utilization of a compact and integrated power unit, such as is typically found in crawler type tractors, and in which such power units include a prime mover, torque converting means driven off one end of the prime mover, an output shaft, and together with main transmission means between the output shaft and the torque converting means lto provide selective forward and reverse drives to the output shaft. Such power units embody oil type clutch and brake means, lubricated from the lubricating system of the power unit, which are operative for clutch- States Patent O Patented .lune Il, 1958 "ice ing or braking an output gear to the output shaft. Such clutch and brake means require infrequent service and have long life under hard usage. ln utilizing la power plant as noted, the cumbersome and unsatisfactory arrangement of clutching and/or braking a cable winding drum, as in the known winch mechanisms is avoided.

The invention further comprehends a drive system in combination with a power unit, as aforenoted, of a bed or supporting frame structure in which a drum supporting shaft is mounted at its opposite ends in the side walls of such a frame structure and with which a rotatable cable winding drum is associated. A drum drive gear is provided for effecting rotation of the cable winding drum and torque transmitting means, such as an endless chain, may extend from the output gear of the power unit to the drum drive gear so as to provide for rotation of the cable winding drum in one direction or the other or for holding the drum against rotation in either direction. In the known power lunits the output shaft has output gears at the opposite ends thereof which is advantageous in the present invention to provide drive source for independently rotating either of a pair of cable winding drums or conjointly rotating both cable winding drums. In a winch mechanism of the present invention, embodying a plurality of cable winding drums, the several drum s-upporting shafts extend transversely of the lside walls of the supporting fra-me or bed and provide a rigidly reinforced frame so that the side walls of the frame may 'be relatively thin as compared to the side walls of the frames of known cranes. If desired the drum supporting shafts may be iixedly mounted t-o the side walls of Ithe frame and with the drums being rotatably mounted on such shafts.

A further important advantage of the present invention resides yin the provision of auxiliary drive means driven from the end of the prime mover of the power unit opposite the end connected with the torque converting means, and which together with suitable torque transmitting means provides for effecting rotation of an auxiliary cable winding drum, and additionally, if desired, for effecting rotation of the platform or bed for a boom or other component which is to be rotated relative to the main frame of the mechanism.

The above and other objects and advantages of the invention will appear from the following detailed description of `a preferred embodiment of the invention shown in the accompanying drawings in which- FIGURE l is a schematic plan View of a drive system for a winch mechanism of the present invention;

FIGURE 2 is an enlarged schematic plan view of a portion of the drive system shown in FIGURE l;

FIGURE 3 is a side elevational View showing the winch frame and an arrangement of drum supporting shafts, cable winding drums, and torque transmitting means for effecting rotation of the cable winding drums;

FIGURE 4 is a front view of the assembly shown in FIGURE 3; and

FIGURE 5 is a perspective view of the winch frame shown in FIGURES 3 and 4.

Referring now to FIGURE 1 of the drawings there is shown a drive system for a winch mechanism of the present invention comprising a power unit, indicated generally at 5, which is supported on a frame or platform, such as illustrated at 6, of a crane or other winch mechanism. The power unit 5 is an assembly of known components and may be of a construction commonly employed in crawler tractors as, for example, in the model AD*6 crawler tractor made and sold by the Allis-Chalmers Mfg. Co. of Milwaukee, Wis. The power unit 5 basically comprises a prime mover '7,- such as an internal Combustion engine, connected at one end to a torque converter 8,

which, in turn, has connection with a transmission gear box 9 providing desired forward and reverse drive ratios to a driven gear 1G which through suitable and known gearing effects rotation of a gear 11 keyed or splined to an output shaft 12. The power unit further incorporates known combination clutch and brake mechanisms '13 and 14 disposed at opposite ends of the output shaft 12, and which, as is known, may be actuated to selectively clutch first 4and second output gears 16 and 17 at opposite ends of the output shaft to the output shaft 12 or to hold or brake such output gears against rotation. In the aforementioned known power units for crawler tractors, the output gears 16 and 17 are provided to effect rotation or non-rotation of associated crawler treads, for driving and steering the tractor as is well known.

It will be understood that the foregoing power unit 5 has been described in its overall essential arrangement of components without going into the many details of construction of the gearing, clutches and brakes which are well known. Of particular importance for the present invention is the combination of clutch and brake assemblies 13 and 14 which are lubricated from the lubricating system of the power unit 5 and require no special lubrieating maintenance other than the normal serving of the power unit.

The platform or frame 6 comprises a pair of vertically spaced apart side walls 2) and 22 with respect to which a first drum supporting shaft 23 extends in transverse rela tion with the shaft 23, which in the embodiment of the invention as shown in FIGURES 3 and 4, is secured in non-rotative relation relative to the side walls 20 and 22 by hub members 24 and 25 to which the opposite ends of the shaft 23 extend and are secured by pins 26. A first rotatable cable winding drum, such as at 27 is associated with shaft 23 and is provided with end tianges 28 and 29 so that a first cable may be wound upon the drum between the end iianges. As best seen in FIGURE 4 the drum 27 has an axially extending hollow drum shaft 36 with there being cylindrical bearing means 32 between the hub shaft 39 and outer surface of the stationary drum shaft 23 to rotatably support the first cable winding drum 27 for rotation on the first drum supporting shaft 23. A first drum drive gear is rigidly secured, as by collar 37, at one end of the cable winding drum 27. First torque transmitting means, such as defined by an endless chain 36, drivingly connects first output gear 16 with the first drum drive gear 35 so that the cable Winding drum 27 may be rotated in one direction or the other from the power unit 5 for :the paying out or reeling in of the cable, or for holding the drum against rotation in the manipulation of a load connected to the first cable wound on the drum.

In many winch mechanisms a plurality of cable winding drums are desirable for carrying out multiple operations and, accordingly, in the present invention there is provided a second drum supporting shaft 40 extending transversely of the side walls 2t) and 22 of the platform frame 6, and which shaft 46 is secured at its opposite ends to the side walls in the same manner as described in connection with the first drum supporting shaft 23. A second cable winding drum 42 is associated with second known supporting shaft 40 in the same manner as aforedescribed in connection with the drum 27. The second drum supporting shaft 40 at its end adjacent the side wall 22 in the embodiment of the invention shown in the drawings has a second drum drive gear 43 fixed thereto and second torque transmitting means, as defined by the endless chain 45, drivingly connects the second output gear 17 with the second drum drive gear 43 so that the second cable winding drum through the power unit 5 and the -aforedescribed mechanisms may be rotated in one direction or the other, or held against rotation, as may be desired, in controlling a second cable wound on the drum 42 in performing an additional winch operation.

According to the present invention and in order to achieve additional winch functions from a single power plant, auxiliary drive means indicated at 50 is provided at the end of prime mover 7 opposite the connection of the latter with the torque converter '8, and from which first auxiliary torque transmitting means, indicated generally at 52, extends to a first auxiliary output gear 55'. An auxiliary drum supporting shaft 58 extends transversely between the side frames 20 and 22, and the opposite ends of the shaft 58 in the illustratedv embodiment of the invention are secured to the side Walls in the manner aforedescribed in connection with the first drum supporting shaft 23. An auxiliary drum drive gear 60 is iixedly se cured to an auxiliary cable winding drum 62 lrotatably mounted on the auxiliary stationary drum supporting shaft 58 in the same manner as aforedescribed in connection with the first and second cable winding drums 27 and 42. The aforementioned first auxiliary torque transmitting means includes an endless chain 65 for connecting the auxiliary output gear 55 with the auxiliary drum drive gear 66 to provide, as will be described, for the rotation of the auxiliary drum 62 in one direction or the other as may be desired. The first yauxiliary torque transmitting means, as best seen in FIGURE l, further includes an endless chain 63 drivingly connecting the auxiliary drive means 56- with a gear 65 keyed to a first auxiliary transmission input shaft 66 of a first auxiliary transmission or gear box assembly 67. The gear box 67 includes a countershaft defining a first auxiliary output shaft 64 to which the first auxiliary output gear 68 is keyed. It will be seen that a gear 70 rotatably mounted on the input shaft 66 has constant meshing engagement with a gear 72 keyed to the first Iauxiliary output shaft 64. Conventional and known clutch means 73 provides for clutching or releasing the gear 70 selectively with respect to the input shaft 66 so that the gear 7 fi, when clutched to the shaft 66, effects rotation of the gear 72 and driving of the first auxiliary output shaft 6ft in one direction. A second gear 76 is also journalled on the input shaft 66 and a second gear 80 is keyed to the first auxiliary output shaft 64. The second gear is drivingly connected with the gear 76 by an endless chain 82. Upon engagement of conventional and known clutch means 83 and disengagement of clutch 73, the gear 76 rotates with the input shaft 66 and through the chain 82 effects rotation of the gear 80 so as to drive the first auxiliary output shaft 64 in the reverse or opposite direction. The auxiliary cable Winding drum 62 may thus be driven in either direction at the will of the operator.

As best seen in FIGURE 2, the first auxiliary output shaft 64 of the first auxiliary transmission means 67 is drivingly connected with a known hydraulic pump assembly connected in a fluid circuit 92 embodying valve means as shown .at 93. The hydraulic pump 90 is of known construction in which upon rotation of the rst auxiliary output shaft 64 in either 0f its directions of rotation, the pump circulates fluid under pressure in opposite directions in the fiuid circuit 92. The valve means 93 comprises a pivoted valve member 95 having a restricted orifice 96 therein which is operative upon flow of fluid in one direction to seat the valve and restrict fiow of fiuid under pressure in the circuit through the metering orifice 96. Upon flow of fiuid under pressure in the iiuid circuit in the opposite direction, the valve 95 is biased to open position to provide for the relative free flow of fluid in the fluid circuit 92.

The hydraulic pump 90, fiuid circuit 92 and valve 93 thus provide for controlling the rate of rotation of the auxiliary cable winding drum 62 by imposing the load of the restricted fiow of fluid under pressure in the tiuid circuit. *In one direction of rotation the auxiliary cable winding drum is virtually unimpeded and in its opposite direction of rotation it is restricted by metering of the fluid in the fluid circuit through the metering port 96. The last related foregoing components may thus be conveniently associated with an auxiliary cable winding drum 62 employed for hoisting and lowering a boom with the hydraulic pump and fluid circuit Iassembly being associated with the lowering of the boom so that it is lowered at a controlled rate. Also, the aforedescribed hydraulic system provides for control of a boom in instances where a neutral is established in the first auxiliary transmission in that the first Iauxiliary output shaft 64 is driven by rotation of the auxiliary cable winding drum 62 so that, `for example, in lowering the boom, the boom may not be accidently dropped at a high and dangerous rate of speed.

Referring again to FIGURE 1, the power take-off from the prime mover 7 through the auxiliary drive means 50 may be advantageously utilized to effect rotation of the supporting platform 6 as, for example, about the axis x as indicated in FIGURES 1 and 3. To this end, second auxiliary torque transmitting means indicated generally at 97 extends from the yauxiliary drive means 50 for effecting rotation of ring gear means 98 connected to the supporting platform 6. Such second auxiliary torque transmitting means comprising an endless chain 97a extending to a gear mounted on a second auxiliary input shaft 99 of `a second auxiliary transmissioin means 100, and from which an output shaft 101 extends to gear means, indicated at 102 for driving a pinion 104 meshing with the ring gear means 98. The second auxiliary transmission 100 comprises a first gear 105 journalled on the input shaft 99 `and having constant meshing engagement -with a gear 106 keyed to the output shaft 101. Actuation of conventional clutch means 107 provides for selectively clutching the gear 105 to the input shaft 99 or freeing the gear 105. A gear 108 is also freely journalled on the input shaft 99 and it has connection by means of a chain 109 to a gear 110 fixed to the second auxiliary output shaft 101. Upon engagement of known and conventional clutch means 115, the gear 108 may be clutched to the input shaft and through the chain 109 effect rotation of the second auxiliary output shaft 101 in the opposite or reverse direction. The selective actuation of clutches 105 or 115 thus provide for the transmission of drive through the second auxiliary torque transmitting means 97 from the prime mover 7 to rotate the ring gear means 9S in one direction or the other and thus dispose the assembly in desired rotative positions. The foregoing drive system thus provides for the selective rotation of the first, second and auxiliary cable winding drums and rotation of the whole assembly about the center of swing indicated at x.

It will be observed from the foregoing that the present drive system provides considerable fiexibility for effecting selective rotation of a plurality of three cable winding drums and rotation of the platform of a winch mechanism from a single prime mover.

It will be understood that cables on the several cable winding drums may be wound in the same or different directions so that two or more of the drums may be rotated to provide the desired reeling in or paying out of cables on the drums in the manipulating of a load connected with the cables.

Referring now to FIGURES 3, 4 and 5, it will be seen that the side walls and 22 are rigidly joined together by the first, second and third drum supporting shafts 23, and 58, respectively, to provide au exceedingly strong yframe which resists bending and distortion and enables the utilization of large diameter and high capacity cable winding drums. The frame structure 6 is further rigidly reinforced by the provision of chamber or casing means such as indicated at 110, 111 and 112 respectively. The chamber 110 is of a con-figuration for enclosing the first output gear 16, first drum drive and connecting chain 36 with the inner peripheral edges of the walls of the chamber being welded to the adjacent wire surface portions of side wall 20. As viewed from the side the chamber means 110 extends angularly upwardly and which together with the inside surface of side wall 20 define a well or oil reservoir 122 at the lower portion ol. thc chamber. Thus, upon rotation of the first output gear 16 to drive the first cable winding drum 27 oil is carried by the chain between the two gears providing for the continuous lubrication of the gears and chain. The second chamber or casing means 111 is mounted adjacent the inside surface of the side frame 22 to enclose the second output gear 17, the second drum drive gear 43 and endless chain 45. The chamber means 111 is also provided with a well 123 formed at the bottom of the chamber and the adjacent inside stirface of the side wall 22.

A third chamber or casing means shown at 112 is secured to the inside surface of the side wall 22 to enclose the auxiliary drum drive gear 6i?, the first auxiliary input gear 55 and the endless chain 65 extending between the gears and with the lower inner portion of the chamber 112 defining an oil well 124 for effecting lubrication of the chain and gears. The opening in the inside walls of the chamber or casing 110., 111 and 112 may be provided with suitable seals to protect the enclosed gears and chains from the weather so that the winch mechanism is protected from damage thereby.

Again, upon reference to FIGURE 4, it will be seen that each of the cable winding drums is provided with an oil filler pipe, as at 150, which as best seen in connection with the cable winding drum 27, extends through a hollow central tubular hub shaft 30 of the drum with there being one or more ports 15S in the hollow shaft to provide for lubricating bearing means 32. The drums may be filled with a large quantity of oil so that the hollow interior of the drums serve as oil reservoir means to maintain a substantial oil supply for lubricating the bearings of the drums in the rotation thereof around the sta tionary drum supporting shafts. The construction described provides a simple way of lubricating the bearing means for the drums and the large storage capacity of the drums requires infrequent checking of the oil levels and addition of oil thereto in the operation of the winch mechanism. lf desired the sever-ai cable winding drums may be provided with means for indicating the oil level or amount of oil in the drums.

While there has been shown and described a preferred embodiment of the invention, it will be understood that various modifications and rearrangements may be made therein without departing from the spirit and scope of the invention.

The invention claimed is:

1. In a drive system for a winch mechanism including a prime mover, torque converting means driven off of one end of said prime mover, an output shaft, main transmission means between said output shaft and said torque converting means to provide selective forward and reverse drives to said output shaft, a first output gear, first clutch means and first brake means between one end of said output shaft and said first output gear for selectively clutching said output shaft to said first output gear upon engagement of said first clutch means and disengagement of said first brake means, or for braking said first output gear against rotation upon engagement of said first brake means and disengagement of said first clutch means, the combination of a first drum supporting shaft, a first rotatable cable winding drum associated with said first drum supporting shaft, a first drum drive gear for rotating said first cable winding drum, first torque transmitting means connecting said first output gear and said first drum drive gear for rotating the latter, auxiliary drive means driven off the other end of said prime mover, an auxiliary drum supporting shaft, an auxiliary rotatable cable winding drum associated with said auxiliary drum supporting shaft, an auxiliary drum drive gear for rotating said auxiliary cable winding drum, first auxiliary torque transmitting means connecting said auxiliary drive means and said auxiliary drum drive gear for rotating the latter, a rotatably mounted supporting platform for supporting said first rotatable cable winding drum and said auxiliary cable Winding drum, ring gear means connected with said supporting platform, second lauxiliary transmission means having a second auxiliary input shaft and a second auxiliary output shaft, means drivingly connecting said second input shaft with said auxiliary drive means, means drivingly connecting said second auxiliary output shaft with said ring gear means, and clutch means for said second auxiliary transmission means to provide selective forward and reverse drives to said second auxiliary output shaft for driving said ring gear means in opposite directions.

2. In the drive system of claim 1 including a second output gear, and second clutch means and second brake means between the other end of said output shaft and said second output gear for selectively clutching said output shaft to said second output gear upon engagement of said second clutch means and disengagement of said second brake means, or for braking said second output gear against rotation upon engagement of said second brake means and disengagement of said second clutch means, the combination of a second drum supporting shaft, a second rotatable cable winding drum associated with said second drum supporting shaft, a second drum gear for rotating said second cable winding drum, and second torque transmitting means connecting said second output gear and said second drum drive gear for rotating the latter.

3. In the drive system of claim 1, including a second output gear, and second clutch means and second brake means between the other end of said output shaft and said second output gear for selectively clutching said output shaft to said second output gear upon engagement of said second clutch means and disengagement of said second brake means for braking said second output gear against rotation upon engagement of said second brake means and disengagement of said second clutch means, the combination of a second drum supporting shaft, a second rotatable cable winding drum associated with said second drum supporting shaft, a second drum gear for rotating said second cable 'winding drum, and second torque transmitting means connecting said second output gear and said second drum drive gear for rotating the latter, said first auxiliary torque transmitting means comprising a first auxiliary input shaft drivingly connected with said auxiliary drive means and a first auxiliary output shaft drivingly connected with said auxiliary drum drive gear, first auxiliary clutch means for said first auxiliary torque transmitting means to provide selective forward and reverse drives to said first auxilary output shaft, iiuid circuit means, hydraulic pump means driven by said first auxiliary output shaft for circulating fluid under pressure in one direction through said iiuid cirn cuit means in one direction of rotation of said first auxiliary output sh-aft and for circulating fluid under pressure in the other direction through said first fluid circuit means in the other direction of rotation of said rst auxiliary output shaft, and valve means in said fluid circuit means providing for free liow of iiuid in one direction therethrough and restricting iiow of fluid in the other direction therethrough.

4. In the drive system of claim 3 the combination therewith of a rotatably mounted boom supporting platform, ring gear means connected with said boom supporting platform, second auxiliary transmission means having a second auxiliary input shaft and a second auxiliary output shaft, means drivingly connecting said second input shaft with said auxiliary drive means, means drivingly connecting said second auxiliary output shaft with said ring gear means, and clutch means for said second auxiliary transmission means to provide selective forward and reverse drives to said second auxiliary output shaft for driving said ring gear means in opposite directions.

5. In a drive system for a Winch mechanism including a prime mover, the combination of auxiliary drive means driven by said prime mover, an auxiliary rotatable cable winding drum associated with said auxiliary drum supporting shaft, an auxiliary drum drive gear for rotating said auxiliary cable winding drum, first auxiliary transmission means having a first auxiliary input shaft and a first auxiliary output shaft, means drivingly connecting said first auxiliary input shaft with said auxiliary drive means, means drivingly connecting said first auxiliary output shaft with said auxiliary drum drive gear, first auxiliary clutch means for said first auxiliary transmission means to provide selective forward and reverse drives to said first auxiliary output shaft, fluid circuit means, hydraulic pump means driven by said first auxiliary output shaft for circulating fluid under pressure in one direction through said fiuid circuit means in one direction of rotation of said first auxiliary output shaft and for circulating fiuid under pressure in the other direction through said fluid circuit means in the other direction of rotation of said first auxiliary output shaft, and valve means in said fiuid circuit means providing for free flow of fluid in one direction therethrough and restricting fiow of fluid in the other direction therethrough.

6. In the drive system of claim 5 the combination therewith of a rotatably mounted boom supporting platform, ring gear means connected with said boom supporting platform, second auxiliary transmission means having a second auxiliary ipput shaft and a second auxiliary output shaft, means drivingly connecting said second input shaft with said auxiliary drive means, means drivingly connecting said second auxiliary output shaft with Said ring gear means, and clutch means for said second auxiliary transmission means to provide selective forward and reverse drives to said second auxiliary output shaft for driving said ring gear means in opposite directions.

References Cited UNITED STATES PATENTS 2,263,064 11/1941 Allin 254--187 2,775,429 12/1956 Ashton M 254-187 2,881,882 4/1959 Gentile 254-187 2,984,455 5/1961 Fischer 254-185 3,158,355 11/196-4 Wilson 254-185 3,244,404 4/1966 Bender 254-185 3,300,189 l/1967 Blount a 254-185 FOREIGN PATENTS 1,144,478 10/1957 France.

EVON C. BLUNK, Primary Examiner.

RICHARD E. AEGERTER, Examiner.

H, C. HORNSBY, Assistant Examiner. 

